Edging machine



27, 946. G. w. JACKSON 0 60 EDGING MACHINE d May 21, 1943 7 Sheets-Sheet? IN VENT 'OR 7 Sheets-Sheet s G. W. JACKSON- EDGING MACHINE Filed May 21, 1945 Aug. 27, 1946.

7 Sheets-Sheet 4 INVENTOR AT RNEY G. W. JACKSON EDGING MACHINE Filed May 21, 1943 GEORGE W JACKSON Aug. 27, 1946.

v V Q Q fi w g @n i E f i NS \Q G. w. JACKSON EDGING MACHINE Filed May 21, 1945 Aug. 27, 1946.

7 Sheets-Sheet 6 Iv v I221 ZIZ ' '1 an 9. 217/, '2/8, Z33

2!? 2 8 INVENTOH GEORGE W. JACKSON Patented Aug. 27, 1946 EDGING MACHINE George W. Jackson, Southbridge, Mass, assignor to American Optical Company, Southbridge, Mass, a voluntary association of Massachusetts Application May 21, 1943, Serial No. 487,907

This invention relates to improvements in machines for edging articles to controlled contour shape and more particularly to machines of this character having automatically functioning parts and method of obtaining said functions.

One of the principal objects of the invention is to rotate an article relative to an abrading wheel for reducing the article to a given contour shape and size whereby the said article is reduced to the contour shape and size desired throughout substantially one complete cycle of movement of said article relative to the abrading wheel with said cycle of movement bein hydraulically controlled.

Another object of the invention is to provide a device for edging articles to given contour shapes and sizes whereby the article may be hydraulically clamped into working position or released with the clamping device being rotatable with the article under hydraulic control as to its extent and speed of rotation relative to the abrading wheel for removing the required amount of material from the article and with the abrading wheel hydraulically oscillated in a direction transversely of the article with the extent of the transverse movement or oscillation of the abrading wheel being variable.

Another object is to provide hydraulicallycontrolled holding means for a device of the character described.

Another object is to provide hydraulically. operated means of the above character intercom nected with an oil feed system having the oil pressure of said system controlled by a variable displacement pump.

Another object is to provide a hydraulically operated power unit for rotating 'thearticle at least throughout one complete cycle of movement and having associated therewith speed reduction means for transferring the power fromsaid hydraulic power unit to the article.

Other objects and advantages of the invention will become apparent from the following description taken in connection with the accompanying drawings and it will be apparent that many changes may be made in the details of construc tion, arrangement of parts and methods shown and described Without departing from the spirit of the invention as expressed in the accompanying claims, I, therefore, do notwish't'o be limited to the exact details of construction, arrangement of parts and methods shown and described as the preferred forms only have been given by way of illustration.

Referring to the drawings:

' 9 Claims. (Cl. 51-101) Fig. 1 is a side elevation of the 'device embodying the invention;

Fig. 2 is a front elevational view of said device;

Fig. Sis a plan view of said device;

Fig. 4 is a sectional view taken as on line 44 of Fig. 6 and looking in the direction indicated by 'the arrows;

Fig. 5 is a fragmentary sectional view taken as on line 5--5 of Fig. 6 and looking in the direction indicated by the arrows;

Fig. 6 is a sectional view taken as on line 66 of Fig. 1 through the operating head of the device;

Fig. 7 is a fragmentary sectional view taken as on line 'l-1 of Fig. 1 through the stone oscillating mechanism of the device;

Fig. 8 is an enlarged fragmentary sectional view taken as on line 8-8 of Fig. '7 and looking in the direction indicated by the arrows;

Fig. 9 is an enlarged fragmentary sectional view taken as on line 99 of Fig. 3 and looking inthe direction indicated by'the arrows;

Fig. 10 is a sectional view taken as on line Ill-l 0 of Fig. 9 and looking in the direction indicated by the arrows;

Fig. 11 is an enlarged fragmentary sectional View taken as on line I l-l l of Fig. 3 and looking in the direction indicated by the arrows; and

Fig. 12 is a schematic view illustrating the hydraulically operating system of the device.

Devices for reducing articles to given contour shapes and sizes are not new in the art, particularly, devices for reducing ophthalmic lenses to desired contour shape and size.

Many attempts have been made to provide devices for reducing a lens to a given contour shape and size through one complete cycle of movement of the lens relative to the abrading wheel but in most instances in the past such devices embodied mechanical or electrical means for accomplishing the desired results. Most prior art devices of this nature were of such characteras to have relatively positively operating parts with no intermediate variable as to the function of said parts. In most instances, the control was mainly directed to means for completing the cycle of movement of the article relative to the abrading wheel with the article held in a fixed position until a given amount of material was removed therefrom whereby a contact was made, in. the instance of electrically operated means,

"with a switch or a similar device which closed as to this operation and in most instances did not produce an article having the desired edge finish. The remaining parts of the device operated in a similar manner to other known devices. It, therefore, is one of the primary objects of this invention to overcome the above difiiculties with such prior art devices through the provision of hydraulically operated means with intermediate controls for clamping the article in operating position, for rotating the article relative to the abrading wheel throughout on complete cycle of movement with intermediate controls for insuring the reduction of said article to proper contour shape and size and to proper edge finish, for controlling the surface shape of the stone during said edging operation and for imparting an oscillatory movement to the stone during said edging.

Referring mor particularly to the drawings wherein like characters of reference designate like parts throughout the several views, the device embodying the invention comprises a base l3 having spaced bearings [4 in which the stone supporting shaft is rotatably supported. The stone [3 is carried by a web I! having a hub l8 secured to the shaft [5 by a set screw or the'like 89. The web I! is provided with an integral flange on one side thereof which overlie one side surface of the stone [6 and with a clamp ring 2| secured to the web by .screws or the like 22 for supporting the stone in operating position on said web.

The shaft [5 has. a hollow bore 23 longitudinally thereof. The said shaft [5 is provided adjacent one end thereof with a spiral gear 24 meshing with a spiral gear 25, said spiral gear 25 is in turn connected with a spiral gear 26 carried by a stud shaft 2-1. The stud shaft 2! is supported within suitable spaced bearings '28 and 29. The stud shaft in turn is provided with a worm gear 30 in mesh with a worm 3| .carried by the'driven shaft of a suitable motor or the like 32,

The above provides the power for rotating the abrading wheel or stone IS with the ratio of the said gearing being such as to give you the proper speed of rotation of the stone.

The spiral gear 25, which is set forth above as being driven by a spiral gear 23, meshing with the gear 24 for imparting a rotary movement to the shaft I5 is so designed that when the said gear 25 rotates, a rotary movement will be imparted to the gear 24 and simultaneous to said rotary movement a thrust action will take place causing said gear 24 to move in a direction lon- I gitudinall of the spiral gear 25 causing the shaft l5 and stone carried thereby to be moved in the direction indicated by the arrow 33. Internally of the hollow bore 23 of the shaft l5 there is a valve stem 34 supported by spaced bushing like members 35 and 3E. The bushing 36 is secured in fixed position internally of the bore 23 and the bushing 35 is fixedly secured to the valve stem 34. The end 31 of the valve stem 34 opposed to the gear 24 is provided with a spring washer 38 secured throughout the periphery thereof as illustrated at 33 to the adjacent end of the shaft I5. The washer 38 is cupped and is adapted to have its cupping characteristics reversed by snapping to one side or the other of a plane extending through the peripheral edges thereof.

The valve stem 34 is provided with a hollow bore with the connecting means 3] for securing the spring washer 38 to the stem func- 4 tioning as stopper means for closing one end of said bore.

The bushing 35 is preferably provided With a scalloped contour forming oil ports between the inner wall of the bore 23 and said bushing. The spring 38 is preferably provided with a plurality of openings 42. The valve stem 34 is provided with an opening 43 communicating with the internal bore 40 of said stem and with the v space between the stem and the bore 23 of the shaft l5. The shaft :5 is provided with an opening 44 communicating with the bore 23 and with a hollow chamber 45 internally of the bearing member 46. The bearing member 46 is connected through a port 41 with an oil line 43.

The bearing I4 has an oil chamber 43 internally thereof and is provided with stop means 50 internally thereof having a portion 5! extending outwardly of the bearing to which a part is pivotally attached as will be described later herein. The base l3 adjacent the end of the shaft I5 having the gear 24 thereon is provided with adjustable stop means 52 extending internally of the bore 23. The stop means 52 is provided with a threaded portion 53 threadedly supported within a sleeve 54. The sleeve 54 is rotatably supported in a bearing 55 formed in the base [3 and has a hand wheel 53 attached by a set screw or the like 51. A suitable key plate 53 secured internally of the base [3 and having a tongue 53 fitting within a longitudinal slot in the stop member 52 is adapted to retain said stop member against rotation when the sleeve 5%, which is threadedly connected with the stop member 52,, is rotated through manipulation of the hand wheel 56. Thi provides means for varying the position of the stop means 52 in a direction longitudinally of the bore 23.

Suitable sealing members or the like 3! and 62 are provided in the respective bearings M which are adapted to prevent oil leakage from the bearings and to simultaneously prevent abra sive particles from entering the hearing.

The device set forth above is for imparting an oscillatory movement to the abrading wheel or stone IS. The function of said device is as follows:

It is first pointed out that the chamber 49 contains oil built up to a given pressure as will be hereinafter described more in detail. When the spiral gear 25 is rotated the gear 24 rotates It is herein .pointed out that the helix angle of the spiral gear 25 is such as to simultaneously urge the gear 24 in the direction of the arrow 33. This causes the shaft 15 and the stone carried thereby to be urged in said direction simultaneous to being rotated. As the shaft l5 moves in the direction of the arrow 33 the valve stem 34 is simultaneously moved in said direction. As the shaft I5 and stem 34 move in said direction, oil in the chamber 49 is forced through the perforations 42 through the port 43 into the hollow bore .40 of the stem. The said oil travels longitudinally of said stem and is exhausted from the end 63 thereof where upon the said oil will flow through the open end 54 of the bore 23 back down into the sump internally of the base 13. This permits the stone to be moved in the direction of the arrow 33. Movement is continued in said direction until the member 31 engages the stop means 50 whereupon pressure will be exerted on the end 31 of an amount sufficient to cause the spring 38 to be moved from its cupped position, as illustrated in Fig. '7, to a reversely cupped position. This causes a Valve stem 34 to be' simultaneously moved in a longtiudinal direction, relative to the shaft l5, by an amount equal to the reverse cupping of the spring 38. This movement of the valve stem 34 causes the port 43 to be moved to a position underlying the bushing 36 thereby closing said port. Simultaneously to this movement the bushing 35 carried by the valve stem 34 will be moved in the direction indicated by the arrow 65 by an amount sufficient to cause theport 44 to communicate with the bore 23 of the shaft [5. Oil forced under pressure through the inlet 48 and flowing through the port 41 into the chamber 45 will thereby travel through the port 44 into the hollow bore 23. The oil will then travel through the ports 4| formed in the periphery of the bushing 36 and will thereby travel through the openings 42 in the spring washer 38 and build up a pressure in the oil chamber 49 of an amount sufficient to overcome the thrust imparted to the gear 24 by the spiral gear 25 and thereby cause the shaft S5 to move in the direction of the arrows 65. Repeated operations of this nature impart oscillatory movement to the stone l6.

The oil inlet 48 is connected through a pipe Line 66 to a pipe line 61 which, in turn, is connected with the exhaust chamber 68 of a variable displacement pump 69. The variable displacement pump comprises a housing having a pump shaft H supported therein by suitable bearings 12, 13 and I4. The pump shaft H has a wabble plate pivotally attached thereto at 16. The pump shaft 1| is provided with a sprocket I1 connected through a sprocket chain 18 to a sprocket 19 carried by the stud shaft 21. As the shaft 21 is rotated 'by the motor 32 the pump shaft H is simultaneously rotated. Thi causes the wabble plate I5 to be simultaneously rotated. Rotatably supported in the bearing 12 and keyed to the pump shaft H there is provided asleeve 80 having a bearing projection Bl thereon adapted to contact an engagement member 82 carried by the wabble plate 15; The key connection of the sleeve 80 with the shaft H i such as to permit the bushing to be moved longitudinally of the shaft. It is to be understood that the bearing 12 also moves with said bushing; the bearing 12 being carried'by a plunger 83 which is slidably supported in a bearing 84. The plunger 83, in v turn, engages a bellows 85 which, in turn, is connected with an oil line 85. The bellows 85 is supported by a threaded cap Bl which is threadedly attached to the housing 70. The oil line 86 is connected with a T 88 see' Fig; 11 which; in turn, is connected with a pressure relief valve 89 and 'a pipe line 93. The pipe line Bllis, in turn, connected through the T 95 to the main oilsupply line see Fig. 8. It is'to be understood that oil is forced under pressure thr-riugh the supply line into the pipe line 90 and, in turn, through the oil line '86. This causes a pressure to be built up in the bellows 85. As the pressure is built up internally of the bellows 85 the said bellows will expand and simultaneously move the plunger 83, hearing 12 and bushing 80 in the direction indicated by the arrow 92. This causes the wabble plate 15 to be tilted about its pivot 16. The amount of said pivot being controlled by the amount of pressure which is permitted to be built up internally of the bellows 85.

Internally of the housing I0 there is slidably supported a plurality of pistons 93 having contact with the wabble plate by spring means 94. The plurality of pistons 93 may be three or more in number and are disposed at given meridional positions in spaced relation with each other about the axis of the pump shaft H. As the wabble plate 15 is rotated the said wabble plate will cause said pistons 93 to be reciprocated in their cylinders 95; Oil is fed internally of the housing 10 by means of an intake pipe line $3 which is connected with a suitable filter 91, as shown in Fig. '7. The oil is merely fed from the sump through the filter 97, into the pipe line 96 and, in turn, inwardly of the housing ill of the variable displacement pump 59. The oil from the pipe line 96 flows inwardly of a chamber 98, as the respective pistons 93 are reciprocated by the wabble plate 15, whereby oil will be drawn inwardly of the pipe line 93 into the chamber 98. This takes place when the respectivevalve ports 99 are in communicating relation with the oil chamber =98 and the respective cylinders 95. Continued rotation of the shaft 1! will cause the valve port I00 formed in said shaft adjacent the valve port 39 to communicate with the exhaust chamber 68 whereupon compression of therespective piston 93 whose port is in communication with the exhaust chamber 68 will cause the oil to be forced outwardly of the cylinder through the supply line 61. This causes a pressure to be built up through said supply line into the parts connected with said supply line, the only part so far described is the stone reciprocating mechanism.

The wabble plate #5 is provided with a bearing plate it! supported by the balls' I02 whereby the wabble plate 15 is rotated relative to the plate Nil which, in'turn, has a bearing contact with the respective pistons 93. The reciprocating pistons 33 function as pump means for building up a pressure in the line 61.

As shown in Figs. 1, 2 and 6, there is pivotally attached to the base 53 a work supporting head M33. The work supporting head is pivotally supported by the pivot bar M34 as best illustrated in Fig. 6. The head it3'is provided with spaced bearings I95 and i536. The bearings I06 rotatably support a shaft IE1! having a bearing pad I08 adjacent one end thereof for engaging the work its and a hand wheel H0 adjacent the opposed end thereof by which the said shaft may be manually rotated. The bearings Hi5 support a tubular shaft l i I in which is slidably supported a clamp spindle H2. The clamp spindle H2 is provided with a key pin H3 which extends through diametrically opposed longitudinal slots H4 formed in the hollow shaft iii. The key pin H3'is alsoadapted to secure a piston H5 to said hollow shaft. Internally of the hollow shaft there is provided a coil spring H6 which'is adapted to normally urge the spindle H2 in a direction outwardly of said hollow shaft. The said clamp spindle H2 is provided with-a bearing pad II! adapted to engage the side of the work 138 oppos'ite'the bearing pad I88. The hollow shaft H I onits end opposed'to the clamp spindle H2 is provided with a suitable former H8. The former H8 is adapted to contact a former shoe H9 in amanner similar to other prior art devices and is the means for controlling the contour shape to which the article is edged. The work supporting'head I33, between the spaced bearings I05, is provided with anoil chamber I2!) in which the piston-H5 is adapted to reciprocate. The oil chamber I25 has openings IZI and I22 on the opposed sides of the piston l l 5. Oil coming from the main variable displacement supply pump 69 through the feed line 61 is directed to the T 9|; The T 91 is connected by a pipe line I39, as illushaust trated' in Fig. '7 to the T HE, see Fig. 6. The T I23 is connected to the pipe line I24 which, in turn, is connected to a flexible hose line I25 which is, in turn, attached to a casing I'Z'. The casing I25 has a port 52's. leading into an open chamber I23. This chamber communicates with a passageway I29 formed in the side portion I30 of the head IE3. The passageway I29 communidates with a valve member ISI rotatably supported in said portion I30. There is also communicati-ng with said valve member a passageway I 32 connected with the opening IZI leading into the oil chamber I20. The valve member also communicates with a passageway I53. The member I25 also has an additional oil chamber I34 therein spaced from the chamber I28. This chamber communicates with the opening I22 adjacent the upper end thereof as illustrated best Fig. 4 and communicates with a passageway I35 leading into the valve 53!. Oil forced under pressure through the hose line I25, into the chamber I25, when the parts are in the position as illustrated Fig. 6, will be directed through the passageway I25 into the valve I3I and, as indicated by the arrow I35, will be directed through said valve member into the passageway 53?. and thereby flow into the oil chamber I23 through. the opening I2 5. This will cause a pres sure to' be built up in said chamber between the adjacent wall and the piston I I5 forcing said piston in the direction indicated by the arrow I31. Due to the fact that the piston is attached to the clamp spindle I212 it will force said clamp spindle against the compression of the spring I It in the direction of said arrow I51 thereby releasing pressure of the pad I I1 on the work I58. Simultaneous to this function, oil on the opposite side of the plunger II 5 will flow through the opening 522,. through the small chamber I34, outwardly through the valve I I, as illustrated by the arrow I38 through the exhaust line I53. This, therefore. relieves the pressure on the side of the piston i=5 opposed to that being built up through the opening I'M. When the valve is rotated throughout substantially a 90 cycle of movement the oil will flow through the passageway I29, through the valve I35, into the smaller of the oil chamit l from said oi'l chamber through the opening I 22 into the oil chamber I20 and cause the pressure to' be built up on that side of the piston 555. When this function takes place the line I52 functions as the exhaust line whereby the; oil pressure will be relieved by the flow of the oil through the opening I2I, through the line I32, valve Iii-i and outwardly through the ex- This provides hydraulic means for clamping or releasing the work between the pads I05 and H1. It is to be understood that the tension of the spring I I 5 is such that it can be easily compressed through the building up of the pressure in the oil chamber I20 through the opening 52 I and is adapted to normally retain the work in clamped relation between the bearing pads when no oil pressure is built up in said chamber I20. On the opposed side of the head, the pipe line I24 is connected through a hose line I40 to an oil chamber IAII formed in said head. The oil chamber I M contains an oil operated motor Hill. This motor comprises a block I 53 in which is supported a plurality of longitudinally movable plungers I 54, The plungers communicate with anoil chamber I which, in turn, communicates with the chamber Ill! through the ports I05. Centrally of the block I53 there is a rotatable shaft M1. supported by spaced bearings I48 and M5. The shaft I41 has rigidly attached thereto a plate I50 disposed at a given angle and adapted to be engaged by the respective plungers WI. This plate I50 has a face plate I5! carried thereby adapted to be immediately engaged by the plungers I4 3 so as to permit rotation of the plate 550 independently of rotation of the plate I5I. The shaft I41 has a valve port I52 formed therein which, upon rotation of the shaft I41, is adapted to cause oil in the chamber IM to be directed through the respective ports It and oil passageways I I-5 progressively and successively as the said shaft M1 is rotated. Simultaneously to this function an additional valve port I55, formed on the side of the shaft I51 opposed to the valve port I52 and in slightly staggered relation therewith, is provided for successively and progressivelv causing the plungers IM to be compressed in communicating relation with suitable exhaust openings I53 formed in the periphery of the'bearing I48 whereby oil will flow from the plunger cylinders through said exhaust openings I53 as indicated by the arrow I54.

As shown in Fig. 6, oil entering the line I40 will pass through the lower port I45, through the chamber I05 and will build up and exert a pressure on the lower plunger I44. This will cause said plunger to exert a pressure on the face plate I5I which, due to the particular angle of said face plate, will cause the plate I50 to be rotated. This causes the shaft I51 to be rotated and due to the provision of a plurality of said plungers its will cause successive plungers to be compressed and others to be exhausted and thereby provide a power drive for rotating the shaft I41.

As shown in Fig. 6, the angle of the plate I50 is 90 out of phase with the actual position at which it will be related with the valve ports I52 andin order to be diagrammatically illustrated. In actual practice, the angle of theplate I55, relative to the valve ports I52 and I55 will be rotated approximately 90 from said illustrated position. The shaft I51 is provided with an eccentric protrusion I55 on which a pair of adjacent gears I51 and I58 are rotatably supported. The gear I58 meshes with an internal gear I59 which normally is free to rotate within the'be'aring I60, see Fig. 5, formed in the head I03. The head I03 adjacent the internal gear I59 is provided with a locking cam IB'I, pivotally supported at I62, having an external manually operable portion I63 by which the cam I5I may be moved to exert a binding pressure on the periphery of the internal gear I59. This cam member IIi'I thereby locks the gear I59 against rotation or will release said gear for rotation, as desired. The gear I51 meshes with an adjacent internal gear I64, see Fig. 6, which is rigidly supported in a hub I65 rotatably carried by the stud I55. The stud I55 is threadedly connected, as illustrated at I51, to the main frame of the head I 03. Mounted on said hub I65 there is a gear I68 which meshes with a gear I69 carried by the shaft Ill'l.

The gear I51 has one tooth more than the gear I50 and the internal gear I55 has one tooth more than the internal gear I59. The purpose of this arrangement is to provide a speed reduction as to the rotation of the shaft I01. This causes the shaft I41 to rotate approximately 1000 to 1 revolutions of the gear I54 thereby causing said gear" I 54, through the gears I68 and I60, to impart the desired speed of rotation to the shaft I01.

The gear I53 has a, gear I10 meshing therewith. The gear I10 is carried by a stud shaft I11 rotatably supported in spaced bearings I12 and I13 formed in a part carried by the head. Adjacent the opposed end of said shaft I1I there is supported a gear I14. This meshes with an idler gear I15 which, in turn, meshes with they gear I15 which is, in turn; carried by the hollow shaft III. This causes the hollow shaft III to be rotated simultaneous to the shaft I01 and through the lock pin II3 imparts a simultaneous rotation to the clamp I I2. Due to the fact, that the former I I8 is carried by the shaft III, the

said former is simultaneously rotated. When it is desired to impart a rotary movement to the gear I64, the gear I59 is clamped against rotation by the cam member I9I. If it is desired to check the rotation of the gear I64 and thereby stop rotation of the shaft I01 the gear I59 is released by the cam member I6I whereupon it is free to rotate and thereby prevent the gear I64 from rotating. When the gear I59 is released by rthe cam member I9I the said shaft I01 may be rotated by the manually operable means IIO.' This permits the article I09 to be rotated for gauge purposes. Suitable resiliently urged stop members I11 areprovided for engaging indentures E18 formed in the lower extremities of the pivoted portions of the head to limit the outward movement of the head in a direction away from the abrading wheel. 7 I a v Referring to Fig. 11, the oil line '90- is connected with the T 9|, as illustrated intFig. 8, as previously described above, which receivesits flow of oil under pressure from a variable displacement pump 69. It has been previouslydescribed that the oil forced through the line 90 passes through the pipe line 86 to the bellows 95, as illustrated in Fig. 8. The T 88 also connects said pipe line 90 to a relief valve 89 having a ball valve member I19 internally thereof. The ball member is urged into closed position by means of a coil spring I90; The spring is compressed by a plunger I8I slidably supported in.

the member 89. The plunger I8I is provided with a contact I82 adapted to engage a bell crank I83. The bell crank I83 ispivotally ;sup-.

ported by the stud see Fig. '7. For ease of operation, the member I83 is connected through a ball bearing I84 to said stud. The bell crank I83 is provided with a hollow arm I85 in which is slidably supported a rack member I86 carrying adjacent its outer end the former II9. In order to permit the rack to be moved longitudinally of the hollow arm I85 and to seal said arm against the entry of dirt, dust and so forth, outwardly of the hollow member there is provided a bellows I81 having a sealed connection I98 with the rack member and a sealed connection I89 with the hollow arm I85. The rack I86 meshes with an idler gear I90 which, in turn, meshes with a gear I9I carried by a manually rotatable member I92. Therotatable member I92 is calibrated on the face I93 thereof and said calibration is registered with a suitable pointer I94 which, through rotation of the mem-- ber I92, causes the rack I86 to be adjusted inwardly or outwardly of the hollow arm I85; This adjustmentis to move the former contact shoe II9 rearwardly or forwardly with respect to the plane of the portion of the abrading wheel which is engaged by the articleto be edged and provides means for controlling the size towhich the article is to be edged. It is .quiteappare'nt that as the former contact shoe H9 isadjusted rearwardly more of the material of the article will Ice-removed from the contour thereof and the size of the article'will be accordingly controlled. Internally ofthe pipe 1111690 there is provided a disc I95 having a restricted opening therein. This disc I 95'is to retard the speed of flow of-the oil through the line 90 leading into the pipe line 86 and valve member 89 and it is primarily for the purpose of avoidingan excessive flow of oil through the valve. The valve member, in addition to the ball valve member I19; is provided with an exhaust opening I96 which, if oil'is forced through the port I91 at a pressure sufficient to force the ball rearwardly and to allow oil to flow through said port I91, the said oil will then be exhausted through the exhaust port I96 and thereby regulatethe'pressure of the oil through the line 89. The line 86, as shown in Fig. 8, is connected with the bellows 85 and is for the purpose of regulating the pressure said bellows 85. This pressure is varied by the mechanism illustrated in Fig. 11 and functions substantially as follows:

As the article I09 is being rotated in engagement with the abrading wheel and the material is being removed from the contour of saidarticle the former I I8 is initially held out of engagement with thecontact shoe II9. the fact that the article I09, of course, is initial- 1y larger in diameter than the finished size desired At this stage the article I09 rotates very slowly and remains in a substantially fixed position relative to the stone until a sufficient amount of the engaged edge of the article I09 is removed to permit the former II8 to engage the contact shoe II9. Continued removal of the material of the article I09 causes a pressure to be exerted on the former shoe II9 through engagemerit of the former shoe II8 therewith. This pressure, through frictional contact of the former II8 with the contact II9, causes the bell crank I83 to be tilted about its pivot 5 I. Through the engagement of the bell crank I83, through the contact I82, this tilting movement Will impart a pressure on said contact and will cause the plunger I8I to, in turn, impart a pressure on the coil spring I80. The coil spring I80 will, in turn, increase the pressure on the ball valve I19 and resist the incoming pressure of the oil by an amount determined by the extent of rocking movement of the bell crank I 83; This in creased pressure on the ball valve I19 thereby in'said direction will cause the bearing member 8I to rock the wabble plate 15 an amount equal to the extent of the movement of the plunger 83. This tilting of the wabble plate 15 will cause an increased stroke of the respective pistons 93 and will increase the speed of flow or pumping of the oil through the port 68 of the pipe line 61. The pipe line 61 is connected with the T 9! which, in turn,'is connected through a pipe line, not shown, to the T I23 and will thereby direct said pumped oil from the line 61 to the pipe line I24 and from said pipe line I24 to the resilient fiexible' hose line I40 and to the oil chamber .MI thereby accordingly increasing the pressure in said chamber I4! and, in turn increasing This is due to 11 the pressure on the respective plungers I44 which are operated by said oil as previously set forth above. This causes the speed of rotation of the shaft M7 to be increased, with the amount of increase depending upon the extent of increase of stroke of the pistons 93 of the pump member 59. This, therefore, causes the speed of rotation of the article I69 to be increased and will more rapidly bring a new and progressive portion of the edge of the article to the abrading wheel for removal. Keeping in mind that the article initially is of a greater size than that desired of the finished article, this will cause the newly presented portion of said article to the abrading wheel to again lift the former I I8 away from the contact shoe I I9, thereby relieving pressure on the coil spring I99 whereby the inherent resiliency of the coil spring will return the bell crank to its initial position. This, of course, relieves pressure on the ball H9 and permits the pressure built up in the line 85 to be relieved whereby oil will flow outwardly through the port I91 and the exhaust port I95 and function as bleeder means for said line 86. This will reduce the pressure in the line 86 and, in turn, reduce the pressure in the bellows 85 and reduce the stroke of the pistons 93. As the material of the article I99 is reduced by abrading and the former I I8 is again permitted to engage the contact shoe H9, a repetitive operation will be performed, which operation, slows down the rotation of the article during the initial abrading and speeds up the rotation of the article when reduced substantially to its final size. t no time during this operation does the article I99 completely stop but through the use of the gearings I51, I58, I59 and IE4 respective y, the speedof rota tion will be reduced to such a state where there is an efiective substantial stopping of rotation ofthe article I99 when a high spot on said article is being removed by the abrading wheel.

With the above arrangement there will be no abrupt change in the speed of rotation of the article but there will be a smooth rhythmic increasing of speed of rotation as the material of the lens is continually being removed by the abrading wheel. If, however, there is a hard spot in the article which is not removed as quickly as the other portions of the edge of the article there will be a relatively abrupt change or decreasing of the speed of rotation of the article through the mechanism described above, but under ordinary circumstances the change of speed resulting through the above described mechanism will be relatively smooth in function resulting in the contour edge of the article having a relative continuous and smooth edge finish. If the article is to be reduced in size considerably and the speed of removal of the edge of the article is relatively slow the said article may move throughout more than one complete cycle of movement but the speed of rotation of the article will be relatively slow during said movement and in most instances will permit the article to be reduced to size in substantially one complete cycle of movement. The function, however, of the device is such that when the article is progressively reduced to size the speed of rotation of the article will synchronously be increased.

The oil which is exhausted through the several exhaust ports mentioned above will flow downwardly under the action of gravity into the sump in the base ofthe machine and will be drawn through the filter 9! before returning to the variable displacement pump 69.

--It is to be understood that during the rotation of the work I I39, as set forth above, the stone or abrading wheel I6 is oscillated by the mechanism shown in Fig. 7 and which has been previously described above. As shown in Figs. 8, 9 and 10, during the oscillation of the abrading wheel I6, there is in constant engagement with said abrading wheel a truing tool I98. The truing tool or hone I99 is carried by a block I99 having a pair of bar members 2% attached thereto. The bar members 299 are slidably supported. in suitable slideways 29! carried by the base of the machine. The block I99 is engaged by a bellows 202 connected through the pipe line 203 to a hone control valve 294. The hone control valve comprises a passageway 295 to which the pipe line 293 is directly connected. The said hone control valve has an inlet port 296 to which the pipe line 6? is connected by means of a suitable three-way fitting 261', as illustrated in Fig. 8. A disc 298 having a restricted orifice therein is positioned in the pipe line 6? adjacent the hone control valve 264 to regulate the flow of oil inwardly of said valve. The inlet port 299 communicates with a valve bore 29!) in which the valve stem 2I9 is rotatably supported. Internally of the hone control valve, there is provided a network of passageways interconnected with each other and with the valve bore 209. This is best seen in Figs. 9 and 10 and comprises a passageway 2 II communicating with the valve bore and connected by a passageway 2 I2 to another passageway 2I3 also communicating with the valve bore 299. The passageway 2 I2 extends transversely from the passageway 2II through the passageway 2| 3 and communicates with a ball valve 2M mounted in a passageway 2E5 communicating with an additional passageway 2H5 also communicating with the valve bore. Opposed to the passageway 2! I there is provided a passageway 2 I? which is adapted to communicate with the passageway 2 through an opening 2I8 when said opening 2H3 is aligned with said respective passageways 2H and 22?. The passageway 2II communicates with a passageway -2I9 which, in turn, communicates with a passageway 229 leading into the valve bore 299 and also communicating with a spring pressed ball valve 22I supported in a passageway 222 communicating with a transversely extending passageway 223 which also communicates with the valve bore 2&9. The passageway 2 il, in addition to communicating with the passageway 2I9, also communicates with an additional passageway 224 which, in turn, communicates with an additional spring pressed ball valve member 225 mounted in a passageway 226. The passageway 226 communicates with a substantially normally disposed passageway 22! which, in turn, communicates with a passageway 228 communieating with a passageway 229 leading to the valve bore 209. The valve stem H9 is provided with a longitudinally disposed groove 23! formed in the side of the valve stem 2H] and adapted to communicate with the passageway 229 in one position of adjustment with the said longitudinal slot 23I extending from said point of communication with the passageway 229 downwardly throughout the length of the valve stem to provide drainage means. The valve stem 2 iii in substantial alignment with the passageways 223 and 2I6 is reduced in diameter to provide a clearane 232- communicating with the longitudinal longitudinal slot 23|. controlling the extent; of pressure on the stone slot 23| whereby oilmay drain from said passageways 2|B and 223 intothe passageway 23|.

The valve stem 2|0'is provided with a flattened side area 233 intermediate its ends adapted to bring about selective communication between the main port 205 and'the respective passageways 2 l3 and 220. The main valvestem is=provided with an eccentrically operated knob 234 having a pointer portion 235 communicating with a plate 236 having suitable indications thereonindicatment of the hone operating mechanism.

-Oil is forced through the line 61 into the passageway 206. As shown in Fig. 10, the valve stem 2|0 is in off position. If the face 233 is rotated to the position indicated by the dash lines 231 the mg the off, dress and hone position of adjustoil passingthrough the port 206 will flow into the passageway 2'|3-, downthroug'h the communicating passageway 2 l2, into the passageway 2| and trolled as to be greater than on the ball 225' whereb the oil entering the respective passage-' ways 2| 1, 220 and 224 willfirst open the ball valve 225 and will flow into the chamber 226 which, in turn, communicateswith the passageways 205 and 221. Since the longitudinal groove 23| in the valve member 2|0, when said valve member is rotated to communicate the port 206with the passageway 2 3, is out of alignment with th passageway- 229 no flow of oil will be permitted through said longitudinal groove 23| and the adjacent side wall of the valve stem will close the opening 229 against'the flow of oil.therethrough.

Oil therefore will not flow through the passage way 221 and will be permitted only to flow outwardl of the passageway 205 through the pipe 203 to the bellows 202. This exerts a relatively low pressure on the stone truing tool I98. This is brought about by reason of the fact that as the pressure is built 'up in the bellows 202, through the newbies throughthe pipe line 203 there will be a simultaneous buildin up of pressure of oil in the various passageways-2| and 2|2 which communicate with the ball valve 2. The ball valve 2! is so controlled by the coil spring pressure imparted thereon as to open when a prede-' termined pressure of the oil is reached in said passageways and will thereby allow the ball valve 2 M to open to permit oil to flow into the chamber 2 5 and from said chamber outwardly of the passagewa 2|6 into the clearance space 232 and to be exhausted from said clearance space into the This provides means for truing tool I98 when the valve stem is adjusted to said above described position. The indicator 235 is now in the dress position. Whenit is desired to hone or true the stone or abrading wheel IS the face 233 of the valve stem is moved to a position whereby the port 206 will communicate with the port-220. V Thiscauses the transversely extending opening 2| 8 in the valve stem to be moved out of communicating relation with the passageways 2| I and 2 H and thereby out of communicating relation with the low pressure valve 2 4. This also moves the longitudinal groove 23| out of alignment with the passagewayv 2-29 with the solid wall of the valve stem 2|0 again functioning to close saidpassageway 229. Oil, therefore, will flow, inwardly of the port 206 intothe 14 passageway 220 and will be directed-from hassageway 220into the passageway 2 9 and into the respective passageways 2|! and 224. Keeping in mind, therefore, that the pressure on the ball valve 22| is much greater than on the ball valve 225 the pressure of the oil will cause the ball valve 225 to again open and cause oil to flow along the passagewa 226 through the pipe line 203 and into the bellows 202. It is to be noted that the ball valve 22| now comes into play and is designed to resist a greater pressure than the ball valve 2| 4 and thereby permits a greater pressure to be built up in the pipe 1ine'203 and into the bellows 202 and will permit a greater pressure to be imparted on the truing tool I98 and to thereby remove and more positively true the face of the abrading wheel I6. The resisting pressure of the valve member 22| is so controlled that when the proper amount of pressure is built up in the bellows 202, to properly hone the abrading wheel, pressure beyond that amount will-cause the ball valve 22| to open permitting the oil to flow through the passageway 222, into the passageway 223 and from said passageway 223 into the spaced area 232 communicating with the longitudinal groove 23| and thereby flow outwardl thereof.

This might be termed an oil bleeding process by which the pressure in th pipe line 203 may be controlled at the different positions of adjustment of the valve stem 2|0 set forth above,

It is to be noted that the spring pressure on the resilient means engaging the ball valves 2M rotatably supported in said bearings, an abrad' and 22| respectively have to be controlled quite carefully in order to permit said bleeding to take place with the proper and desired honing operations. The pressure on the springs for the respective ball valves may be varied by adjustment of the various nut-like members 238 whereby the suitable function of said valve members may be obtained. It is to be noted that the pressure is substantiall continuous on the stone truing de vice |98either when in dressing or honing position and the ball valve 225 functions to prevent backward flow of oil from the bellows during the dressing or honing operation. This. provides means for more positively controlling thecontour shape of the abrading wheel l6.

. Whenthe indicator. 235 is set to off position the face 2330f the valve stem 2|0 will be in a position such as indicated in full line in Fig. 10.

This will shunt the flow of oil through the feed,

line.6'|. The longitudinal slot 23| will now be aligned with the passageways 229, 228 and 221 communicating with opening 226 and pipe line 203. This will allow the oil pressure built up in the bellows 202 to be relieved, From the foregoing description it will be seen that hydraulically controlled means are provided for oscillating the abrading wheel l6; for impartingja rotary movement to the work |09 under variable speeds according to the above description, for hydraulically clamping or releasing the work between the clamp 'pads I08 and Ill and for hydraulically controlling the stone truing tool |90.

Having described my invention, I claim:

1. In a lens edging machine the combination of a base having spaced bearings, a hollow shaft ing wheel attached to the shaft and a head pivotally attached to the base for supporting a lens for movement toward and away from the abrading wheel, said hollow shaft having a valve stem slidably supported internally thereof, spring washerlike means secured to said valve stem and to the adjacent end or the hollow shaft for con:

trolling the position of adjustment of the valve stem longitudinally of the hollow bore of the shaft, said shaft having a gear member adjacent its end opposed to the spring washerlike means meshing with'a rotating spiral gear, said bearing means adjacent the spring washerlike means having an oil chamber therein, means for feeding oil through the hollow shaft into the oil chamber for building up an oil pressure in said oil chamber of an amount sufficient to cause the hollow shaft and abrading wheel to move in one direction with said spiral gear being adapted to continuously tend to urge the hollow shaft and abrading wheel in the opposite direction.

2. In a lens edging machine the combination of a base having spaced bearings, a hollow shaft rotatably supported in said bearings, an abrading wheel attached to the shaft and a head pivotally attached to the base for supporting a lens for movement toward and away from the abrading wheel, said hollow shaft having a valve stem slidably supported internally thereof, spring washerlike means secured to said Valve stem and to the adjacent end of the hollow shaft for controlling the position of adjustment of the valve stem longitudinally of the hollow bore of the shaft, said shaft having a gear member adjacent its end opposed to the spring washerlike means meshing with a rotating spiral gear, said bearing means adjacent the spring washerlike means having an oil chamber therein, means for feeding oil through the hollow shaft into the oil chamber for building up an oil pressure in said oil chamber of an amount sufficient to cause the hollow shaft and abrading wheel to move in one direction with said spiral gear being adapted to continuously tend to urge the hollow shaft and abrading wheel in theopposite direction and means for automatically relieving the pressure in the oil chamber at a given position of movement of the hollow shaft and abrading wheel against the action of the spiral gear whereby the spiral gear will urge the hollow shaft and abrading wheel in the opposite direction to a given position whereby the oil pressure will again build up in the oil chamber.

3. In a device of the character described the combination of a rotatably supported abrading wheel, a work supporting head mounted for movement toward and away from the abrading wheel, means on said head for supporting workholder spindle means, ahydraulically operated power unit, motion transfer means between said power unit and the workholder spindle means for causing said workholder spindle means and work to be continuously rotated, a former carried by said spindle means adapted to engage a contact shoe, a fluid pressure line connected with said hydraulic power unit and means in said fluid line responsive to the movement on the contact shoe through engagement thereof by the former during the abrading of the work for regulating the speed of rotation of the hydraulically operated power unit.

4. An edging machine comprising a rotating abrading wheel, means for supporting work for rotary movement relative to the abrading wheel, former means on said work support for controlling the path of movement of the work relative to the wheel, means for causing said work support to be rotated, adjustable means having a contact shoe for engagement with the former, a fluid pump, conduit means for connecting said fluid pump with said means for imparting a rotary movement to the work support and with the means having the contact shoe thereon, said conduit means connecting the pump with the means supporting the contact shoe having fluid flow control means associated therewith which when the material of the work in engagement with the abrading wheel has been removed by a predetermined amount and the former exerts a pressure on the contact shoe said fluid flow control means will be automatically operated to cause the pump, through its conduit connection with the means for rotating the work support and work, to cause the speed of rotation of said means for rotating the work to be varied according to the Variation of the pressure of the former on the contact shoe. I

5. In a device of the character described the combination of an abrading wheel supported for rotary and oscillatory movement, a work supporting head pivotally supported for movement toward and away from the abrading wheel, rotatable clamp means onsaid head for supporting the work and for supporting a former for simul taneous rotation with said work, means for supporting a contact shoe, a honing device for engaging the abrading surface of the abrading wheel, hydraulically operated means associated with the support for the abrading wheel for imparting an oscillatory movement to said wheel, hydraulically operated means functioning cooperatively with the clamp for supporting the work, hydraulically operated means for rotating said clamp means and the former carried thereby, hydraulically operated means for controlling the movement of the honing device toward and away from the abrading wheel, a fluid pump, means for connecting said fluid pump with said various hydraulically operated means and means correlated with said various means connecting said fluid pump with said hydraulically operated means and with the former support for effecting a cooperative function of said various hydraulically operated means whereby said bydraulically operated means function in proper sequence, withthe hydraulically operated means for rotating the work being responsive to varying pressure of the former on the contact shoe for varying the speed of rotation of the work relative to the abrading wheel according to the amount of material to be removed from the work immediately in engagement with the abrading wheel.

6. In a device of the character described the combination of a rotatably supported abrading wheel, work support means embodying a pair of clamp spindles, a former carried by one of said clamp spindles, a support having a contact shoe for engaging the former, gear means carried by the respective clamp spindles, a train of gears for interconnecting said gear means for simultaneous rotation thereof, a hydraulic motor embodying a plurality of plunger-s successively and progressively moved under hydraulic pressure imparted thereto, an angled disc-like member adapted to be engaged by said plungers and to be caused to rotate under the hydraulic pressure of said plungers, reduction gear means interconnected with said rotating disc and the train of gears for imparting the rotary movement to the clamp spindles, fluid pressure means associated with said hydraulic motor and with the means for supporting thev contact shoe with the pressure of the fluid directed to said hydraulic motor being controlled according to the pressure of the former on the contact shoe whereby the speed of rotation of the motor and therefore '17 the speed of rotation of the work will be varied according to the varying degrees of pressure of the former on the contact shoe.

7. An edging machine comprising a rotating abrading wheel, means for supporting work for rotary movement relative to the abrading wheel, former means on said work support for controlling the path of movement of the work relative to the wheel, hydraulically operated power means interconnected with the Work support for causing said work support to be rotated, adjustable means having a contact shoe for engagement with the former, a fluid pump, conduit means for connecting said fluid pump with said means for imparting a rotary movement to the work support and with the means having the contact shoe thereon and means responding to variation of pressure of the former on the contact shoe for varying the fluid presure on the hydraulically operated means and thereby varying the speed of rotation of the work relative to the abrading wheel according to the amount of material to be removed from the work when in engagement with the abrading wheel.

8. A device for reducing an article to a desired contour shape and size comprising rotatably supported abrading means, a head pivotally supported on suitable means for movement toward and away from the abrading means, rotatable clamp means carried by said head for clampingly supporting the article for engagement with the abrading means, means for imparting a driving force to said clamp means for continuously rotating the article, means for oscillating the head about its pivotal support in timed relation with the rotation of the clamp means, and means including a variable displacement hydraulic pump and a hydraulic control valve for con- 18 trolling the output of said pump for simultaneously regulating the magnitude of said driving force in accordance with the amount of material being removed from that portion of the article in immediate engagement with the abrading means, whereby the rotation of the article relative to the abrading means will be accordingly controlled.

9. In a lens abrading machine the combination of a base having spaced bearings, a longitudinally slidable and rotatable shaft carried by said bearings for rotatably supporting an abrading wheel, a source of power, a gear system adja cent one of said bearings connecting said shaft with said source of power for rotating said shaft, means for building up a hydraulic pressure in the other of said bearing means, said gear system being so constructed as to cause said shaft to move longitudinally of the bearings in a direction toward the bearing having means for building up a hydraulic pressure therein during the rotation of said shaft, means operably functioning to build up a hydraulic pressure in said latter bearing, upon the completion of a desired amount of longitudinal movement of said shaft, of an amount suflicient to overcome the longitudinal movement of the shaft caused by the gear system and for moving said shaft in a direction opposed to the movement introduced by said gear system and means for relieving said hydraulic pressure upon movement of said shaft in said direction a controlled amount whereby the gear system will again move said shaft in said first mentioned direction with the movements of said shaft introducing an oscillatory movement to the abrading wheel in alternate and successive sequence.

GEORGE W. JACKSON. 

